JPH11153180A - Cylindrical vibration control assembly and its manufacture - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve extraction resisting force of an externally inserting cylinder fitting from an outer cylinder member in simple structure on a cylindrical vibration control assembly in structure constituted by connecting a shaft member and the outer cylinder member by a main body rubber elastic body and externally fitting and fixing the externally inserting cylinder fitting on the outer cylinder member. SOLUTION: A recessed part 90 recessed inward is formed on a formation side end part of a collar part 34 on an outer cylinder member 14, while an engagement part 92 bent inward toward the recessed part 90 is formed on an externally inserting cylinder fitting 19. Consequently, it is possible to provide extraction resisting force of the externally inserting cylinder fitting 19 from the outer cylinder member 14 by formal engaging force or friction of these recessed part 90 and engagement part 92.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cylindrical anti-vibration assembly which is advantageously used as a member mount, a body mount, and the like in an automobile, and more particularly, to a shaft member and an outer cylindrical member which is spaced apart from the outer peripheral side of the shaft member. The present invention relates to a tubular anti-vibration assembly having a structure in which an outer tubular member is externally fitted and fixed to the outer tubular member while being connected by a rubber elastic body, and an advantageous manufacturing method thereof.

[0002]

2. Description of the Related Art Conventionally, as one type of a vibration-proof connecting body or a vibration-proof supporting body interposed between members constituting a vibration transmission system,
JP-A-8-177945 and JP-A-9-14331
As described in Japanese Patent Application Laid-Open Publication No. H10-207, an outer cylinder member attached to the other member to be vibration-isolated and connected to the outer peripheral side of a shaft member attached to one member to be vibration-isolated and connected, A cylindrical rubber body is formed by interposing a rubber elastic body between the shaft member and the outer cylinder member to elastically connect them, and furthermore, externally fitting an outer cylinder to the outer cylinder member so as to be fitted and fixed. BACKGROUND OF THE INVENTION Shaking assemblies are known. Further, in such a tubular anti-vibration assembly, a flange portion is formed on an outer peripheral portion of the outer cylindrical member at one end in the axial direction, and the outer cylindrical member is connected to the other member to be vibration-isolated by the flange portion. And a stopper mechanism for buffering and limiting the relative displacement of the shaft member and the outer cylinder member in the axial direction. Further, the outer tube fitting is used as a bracket having, for example, mounting legs protruding on the outer peripheral surface thereof, or is formed of a rubber elastic body as shown in the above publication. It can be advantageously used as a lid member or the like that covers the opening of the pocket to form a fluid chamber in which the incompressible fluid is sealed.

[0003] Such a tubular anti-vibration assembly is specifically adopted as, for example, a vehicle body mount, a member mount, a subframe mount, a cab mount, or a suspension bush such as a strut bar cushion. obtain.

In such a tubular anti-vibration assembly, the outer tube member is fitted to the outer peripheral surface of the outer tube member by reducing the diameter of the outer tube member after the outer tube member is inserted into the outer tube member. However, there has been a problem that it is difficult to obtain a sufficient resistance to the pulling force applied in the axial direction, that is, a pull-out resistance, only by the radial fitting force to the outer cylinder member. That is, on the flange side, which is the direction of extrapolation with respect to the outer cylinder member, a sufficient removal resistance can be ensured by contact with the flange section, but in the axial direction opposite to the outer cylinder member, Since there is no effective means for effectively restricting the relative displacement of the outer cylinder to the member, there has been a problem that it is difficult to sufficiently secure load resistance and reliability in the axial direction.

[0005] In order to secure the pull-out resistance of the outer tube member to the outer tube member, a flange portion is formed at the axial end of the outer tube member to extend outward in a direction perpendicular to the axis. It is conceivable that the outer peripheral edge of the flange portion is fixed by caulking to the outer peripheral edge of the flange portion while being overlapped with the flange portion of the outer cylinder member. And it is necessary to caulk the caulking part, and special equipment and processes are required for this.Therefore, significant deterioration in manufacturability and cost is inevitable, and this is not an effective means. Was.

[0006]

The present invention has been made in view of the above-mentioned circumstances, and an object thereof is to solve an axial direction of an externally inserted cylindrical metal fitting externally fixed to an outer cylindrical member. To provide a cylindrical anti-vibration assembly having a novel structure capable of advantageously securing the pull-out resistance of the above with a simple structure and excellent manufacturability, and a good method of manufacturing such a cylindrical anti-vibration assembly Is to provide.

[0007]

An object of the present invention is to provide an outer tubular member which is spaced apart from the outer peripheral side of a shaft member and has a flange at one opening peripheral edge in an axial direction. Is disposed, and a main rubber elastic body is interposed between the shaft member and the outer cylinder member, so that the shaft member and the outer cylinder member are elastically connected. A cylindrical anti-vibration assembly in which an external cylindrical fitting is externally inserted and fixed with respect to an axial end of the outer cylindrical member on which the flange is formed, A concave portion that is recessed inward in the direction perpendicular to the axis is formed, and is bent inward in the direction perpendicular to the axis toward the concave portion with respect to the axial end portion located on the side of the flange portion of the outer tube. In a cylindrical vibration isolating assembly having a structure in which the engaging portion is formed.

In the cylindrical vibration isolating assembly having the structure according to the present invention, when the pull-out force from the outer cylindrical member is applied to the outer cylindrical member, the concave portion of the outer cylindrical member and the outer cylindrical member are separated from each other. With the engagement portion of the insertion tube, the pull-out resistance due to the locking force or the frictional force is effectively exerted. Moreover, such a mechanism for improving the pull-out resistance can be realized by simply performing the shape processing on the outer cylinder member and the outer cylinder member without requiring any additional special members or special parts. Therefore, it can be advantageously realized under excellent manufacturability and cost.

It is desirable that both the concave portion of the outer cylinder member and the engaging portion of the outer tube fitting be formed continuously over the entire circumference in the circumferential direction. Greater pull-out resistance can be imparted to the metal fitting and the outer cylinder member, but one or two or more such concave portions or engaging portions may be provided in the circumferential direction with a length of one circumference or less. Further, the outer tube fitting may be configured as a bracket integrally formed with legs or the like for attaching to the member to be vibration-isolated.

Further, the present invention can be advantageously applied to a solid type cylindrical vibration damping assembly which exerts a vibration damping effect exclusively by the elastic properties of the main rubber elastic body. Can be applied to a liquid-filled cylindrical vibration damping assembly in which a vibration damping effect is obtained based on a flow action such as a resonance action of the incompressible fluid. In this case, for example, a pocket portion that opens to the outer peripheral surface is formed with respect to the main rubber elastic body, and the outer cylindrical member is fitted and fixed to the outer cylindrical member via a seal rubber layer. Accordingly, a structure in which the opening of the pocket portion is covered in a fluid-tight manner to form a fluid chamber in which an incompressible fluid is sealed is suitably adopted. In short, in the tubular anti-vibration assembly having such a structure, the outer tube fitting is configured as a lid member that seals the fluid chamber filled with the incompressible fluid. By sufficiently securing the pull-out resistance against the outer cylinder member, the sealing performance of the sealed fluid can be improved.

The seal rubber layer interposed between the outer cylindrical member and the fitting surface of the outer cylindrical member is integrally vulcanized on the outer peripheral surface of the outer cylindrical member or the inner peripheral surface of the outer cylindrical member. Desirably, it is molded. Further, when such a seal rubber layer is also interposed between the concave portion of the outer cylinder member and the engaging portion of the outer cylindrical member, the concave portion and the engaging portion do not overlap in the axial direction. Also, when a pulling force is applied between the outer tube fitting and the outer tube member, an effective compressive force is exerted on the seal rubber layer between the concave portion and the engaging portion, so that a locking action or friction is exerted. The pull-out resistance based on the action can be effectively exerted.

Further, as described above, for example, in the case where a seal rubber layer is provided, it is not always necessary to overlap the concave portion with the engaging portion in the axial direction. By being positioned in the recess, the engagement portion and the recess are overlapped with each other in the axial direction. Thereby, the locking action between the engaging portion and the concave portion can be effectively exerted, and the pull-out resistance of the outer tube fitting to the outer tube member is more effectively exerted.

Further, in the cylindrical vibration damping assembly having the structure according to the present invention, in the outer tubular metal fitting, the engaging portion is formed continuously over the entire circumference in the circumferential direction. A structure in which a flange portion extending outward in the direction perpendicular to the axis is integrally formed with the peripheral portion of the opening on the side where is formed, and the flange portion is superimposed on the flange portion of the outer tubular member,
It can be suitably adopted. In the cylindrical anti-vibration assembly having such a structure, the concave portion and the engaging portion are formed over the entire circumference, so that the pull-out resistance of the outer cylindrical member to the outer cylindrical member is more effective. In addition to the fact that the flange portion is superimposed on the flange portion, the strength of the flange portion can be improved. In addition, since the engagement portion is formed on the outer cylinder, the inner diameter of the flange is smaller than the outer diameter of the central portion of the outer cylinder. Even when the bent portion (corner) between the portions is provided with a radius, when the outer tube fitting is press-fitted into the mounting hole provided in the member to be vibration-isolated and connected, the radius is attached. Since the formed corner abuts on the peripheral wall of the mounting hole, it is possible to prevent the flange from being sufficiently intimately contacted with the peripheral wall of the mounting hole, and a stable mounting state can be advantageously achieved. .

A feature of the present invention relating to a method of manufacturing the cylindrical vibration isolator having the above structure is as follows.
After externally inserting the outer cylindrical member into the outer cylindrical member vulcanized and bonded to the outer peripheral surface of the main rubber elastic body, the outer cylindrical member is reduced in diameter and fitted and fixed to the outer cylindrical member. In this case, the outer cylindrical member is bent inward in the direction perpendicular to the axis by increasing the diameter reduction amount at the axial end portion from the axial center portion of the outer cylindrical member, and the outer diameter is reduced by exerting the reduced diameter force on the outer cylinder member. A method for manufacturing a tubular vibration-isolating assembly, wherein a concave portion in a tubular member and an engaging portion in an external tubular fitting are formed simultaneously.

According to the method of the present invention, it is not necessary to form a concave portion in the outer cylinder member in advance, and the concave portion is formed simultaneously with the formation of the engaging portion in the outer cylinder. Therefore, the concave portion and the engaging portion can be advantageously and easily formed with shapes corresponding to each other. In addition, since the formation of the concave portion and the engaging portion can be simultaneously performed by the drawing process for fitting and fixing the outer tube member to the outer cylindrical member, a special process is required for forming the concave portion and the engaging portion. It is possible to realize extremely excellent manufacturability.

Incidentally, it is a matter of course that the cylindrical anti-vibration assembly having the structure according to the present invention can be manufactured by a method other than the method of the present invention. Specifically, for example, a flange portion and a concave portion are formed in advance, and the outer cylinder member vulcanized and bonded to the outer peripheral surface of the main rubber elastic body.
After the outer tube fitting is externally inserted, the engaging portion may be formed by bending the open end of the outer tube member inward toward the concave portion.

[0017]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, in order to clarify the present invention more specifically, an embodiment of the present invention will be described in detail with reference to the drawings.

First, FIGS. 1 and 2 show an automobile suspension member mount 1 according to an embodiment of the present invention.
0 is shown. The mount 10 has an inner cylindrical member 12 as a shaft member and an outer cylindrical member 14 as an outer cylindrical member arranged at a predetermined distance in the radial direction from each other. Both end portions are elastically connected by the first main rubber elastic body 16 and the second main rubber elastic body 18, and the outer cylindrical fitting 19 is further inserted into the outer cylindrical fitting 14. Externally fitted and fixed. As shown in FIG. 3, the mount 10 has a state in which the up-down direction in FIG. 1 is the vehicle up-down direction and the up-down direction and the left-right direction in FIG. , Inner tube fitting 1
2 is bolted to a rod 22 erected on a body body 20 of the vehicle, while the outer tube fitting 19 is press-fitted and fixed to a mounting hole 28 of a mounting sleeve 26 provided on a suspension member 24. The suspension member 24 is interposed at a portion where the suspension member 24 is attached to the body body 20. In the mounted state of the mount 10, as shown in FIG. 4, the body sharing load is exerted between the inner tubular fitting 12 and the outer tubular fitting 19, so that the first and second loads are applied. Body rubber elastic body 16, 18
Is elastically deformed, and the inner cylinder fitting 12 and the outer cylinder fitting 19 are positioned relative to each other by a predetermined amount in the axial direction. Further, in the following description, the vertical direction refers to the vertical direction in FIG. 1 in principle.

More specifically, the inner cylinder fitting 12 has a cylindrical shape, and an annular radial projection 30 that projects radially outward is integrally formed at the upper end in the axial direction. . An outer cylinder 14 is coaxially arranged around the inner cylinder 12 at a predetermined distance radially outward. The outer cylinder 14 has a cylindrical shape whose axial length is less than half the length of the inner cylinder 12.
A flange 34 extending radially outward is integrally formed at the upper end in the axial direction. And the outer tube fitting 14 is
The upper end in the axial direction is the radial projection 3 of the inner cylinder fitting 12.
It is disposed in a state where it is located below the zero by a predetermined amount.

A first main rubber elastic body 16 is interposed between the inner cylinder fitting 12 and the first outer cylinder division fitting 32. The first main rubber elastic body 16 is interposed between the radial end of the inner cylindrical fitting 12 on the radial projection 30 side and the end of the outer cylindrical fitting 14 on the flange 34 side. Is formed in a tapered cylindrical shape which is inclined downward in the axial direction from the outer cylindrical fitting 14 side. Thereby, the first main rubber elastic body 16 is compressed and deformed when a body load is input, so that excellent durability is exhibited. A stopper rubber 36 protruding upward is formed on the flange portion 34 of the outer tube fitting 14, and as shown in FIG. 4, as shown in FIG. However, by being brought into contact with the body main body 20 via the stopper rubber 36, the relative displacement amount of the outer cylinder 14 relative to the inner cylinder 12 in the axially upward direction (bound direction) is limited. ing.

In short, the first rubber elastic body 16 is
An inner cylindrical member 12 is vulcanized and bonded to the inner peripheral surface thereof, and an outer cylindrical member 14 is vulcanized and bonded to the outer peripheral surface thereof. A first integrated member including the inner cylindrical member 12 and the outer cylindrical member 14 is provided. It is formed as a vulcanized molded product 37. Note that a first seal rubber layer 38 is formed on substantially the entire inner peripheral surface of the outer cylinder fitting 14.

Further, a partition rubber 40 is provided between the inner cylinder fitting 12 and the outer cylinder fitting 14. The partition rubber 40 has a substantially cylindrical shape, the upper end in the axial direction is bent inward in the radial direction, and a metal fitting sleeve 42 is vulcanized and bonded to the inner peripheral surface. On the other hand, the lower end in the axial direction is bent outward in the radial direction, and the orifice tube fitting 44 is vulcanized and bonded to the outer peripheral surface.
In short, the partition rubber 40 is formed as a second integrally vulcanized molded product 46 having the fitting sleeve 42 and the orifice tube fitting 44.

The fitting sleeve 42 has a small-diameter cylindrical shape and has a slightly larger diameter in the upper portion in the axial direction, and a thin second seal rubber is provided on the inner peripheral surface of the large-diameter portion. A layer 48 has been formed. Then, the fitting sleeve 42 is press-fitted into the inner cylinder fitting 12 and is fluid-tightly fitted and fixed to the inner cylinder fitting 12 with the second seal rubber layer 48 interposed therebetween. On the other hand, the orifice tube fitting 4
Reference numeral 4 has a substantially large-diameter cylindrical shape, and has a groove-shaped cross section extending in the circumferential direction by bending both ends in the axial direction radially outward. Is provided with a peripheral groove 50 extending continuously. The orifice tube fitting 44 is inserted into the outer tube fitting 14 and is fluid-tightly fitted and fixed to the outer tube fitting 14 with the first seal rubber layer 38 interposed therebetween. Further, by this, the opening of the peripheral groove 50 is covered with the outer tube fitting 14, so that the orifice passage 52 extending in the circumferential direction between the orifice tube fitting 44 and the outer tube fitting 14 is formed.

Further, a metal sleeve 54 is press-fitted to the lower end side in the axial direction of the inner cylinder fitting 12 and is externally fitted and fixed. The metal sleeve 54 has a cylindrical shape having an axial length substantially half of that of the inner cylindrical fitting 12, and has a slightly larger diameter at the lower end in the axial direction. A layer 56 is formed, and is fitted and fixed to the inner cylinder fitting 12 in a fluid-tight manner.

Outside the metal sleeve 54 in the radial direction, the outer tube fitting 19 is disposed coaxially at a predetermined distance and coaxially. The outer tube fitting 19 has a cylindrical shape slightly larger in diameter than the outer tube fitting 14, and
It has substantially the same axial length as the inner cylinder fitting 12.
Further, both ends in the axial direction of the outer tube fitting 19 are positioned so as to protrude outward in the axial direction from both ends in the axial direction of the metal sleeve 54, and at the upper end thereof, radially outward. Spreading annular plate-shaped flange portion 58
On the other hand, at the lower end in the axial direction of the outer tube fitting 19, an annular flange 60 extending inward in the radial direction is integrally formed.

Further, a second rubber elastic body 18 is interposed between the metal sleeve 54 and the outer tube fitting 19. The second main rubber elastic body 18 has a thick cylindrical shape as a whole, and has a metal sleeve 54 on the inner peripheral surface and an outer tube fitting 19 on the outer peripheral surface, each of which is vulcanized and bonded. It is formed as three integrally vulcanized molded products 62. A thin fourth seal rubber layer 64 is formed on the inner peripheral surface of the outer tube fitting 19 over substantially the entire surface.

The upper part in the axial direction of the outer tube fitting 19 is externally inserted into the outer tube fitting 14 and is externally fixed in a fluid-tight manner with the fourth seal rubber layer 64 interposed therebetween. Thereby, the second main body rubber elastic body 18 is interposed between the inner cylinder fitting 12 and the outer cylinder fitting 14 at the lower end side in the axial direction of the inner cylinder fitting 12, so that the inner cylinder fitting 12 and the outer The tubular metal fitting 14 is elastically connected at both axial ends by a first main rubber elastic body 16 and a second main rubber elastic body 18.

Further, on the outer peripheral side of the inner cylindrical metal fitting 12, a pocket portion which is located between the axially opposed surfaces of the first main rubber elastic body 16 and the second main rubber elastic body 18 and opens to the outer peripheral surface. 66 is formed, and the opening of the pocket portion 66 is covered in a fluid-tight manner by the outer tube fitting 19, so that an incompressible fluid is sealed inside and the fluid chamber sealed to the external space. 68 are formed. In addition, as the sealed fluid, water, alkylene glycol, polyalkylene glycol, silicone oil, or the like is preferably adopted. In particular, in order to effectively obtain a vibration damping effect based on the resonance action of the fluid, 0.1 Pa · Those having a viscosity of not more than s are suitably employed.

Further, the fluid chamber 68 is formed in the axial direction by a partition rubber 40 disposed at an axially intermediate portion between the first main rubber elastic body 16 and the second main rubber elastic body 18. The upper part and the lower part are fluid-tightly divided into two parts. Thus, a first annular fluid chamber 70 is formed on the first rubber elastic body 16 side with the partition rubber 40 interposed therebetween. A second annular fluid chamber 72 is formed on the second rubber elastic body 18 side. The first annular fluid chamber 70 and the second annular fluid chamber 72 are communicated with each other through an orifice passage 52 extending a predetermined length in the circumferential direction.
Fluid flow between 0,72 is allowed.

Thus, the first annular fluid chamber 70 and the second annular fluid chamber 72 receive an axial vibration between the inner cylindrical fitting 12 and the outer cylindrical fitting 19 (outer cylindrical fitting 14). In this case, a relative change in the internal pressure is caused, and based on the relative internal pressure difference, the first annular fluid chamber 70
A fluid flow through the orifice passage 52 is generated between the first annular fluid chamber 72 and the second annular fluid chamber 72. As a result, as is well known, an anti-vibration effect such as a low dynamic spring effect is exerted on the basis of a flow action such as a resonance action of the fluid caused to flow through the orifice passage 52. It is. As is well known, the vibration damping effect exerted based on the fluid flow action is tuned by adjusting the length, cross-sectional area, and the like of the orifice passage 52 according to the vibration frequency for vibration damping. It is possible.

Further, the second rubber elastic body 18 is located on the outer peripheral side in a radial direction facing the vehicle front-rear direction with the metal sleeve 54 interposed therebetween. A pair of bulges 74, 74 having a circumferential length and extending axially downward from the upper end surface in the axial direction along the inner peripheral surface of the outer tube fitting 19 are formed. A sufficiently soft spring characteristic is exerted against an input load in the radial direction where the pair of bulges 74 and 74 are opposed to each other. The spring ratio between the radial direction and the radial direction perpendicular thereto, in other words, the spring ratio between the vehicle front-rear direction and the vehicle left-right direction is set to be sufficiently large. Therefore,
In the radial direction that is the vehicle left-right direction, hard spring characteristics are exhibited, and excellent steering stability can be ensured. In the radial direction that is the vehicle front-rear direction, sufficiently soft spring characteristics are exhibited, and the harshness Thus, the anti-vibration performance is improved, and excellent riding comfort is achieved.

Further, a stopper ring 76 made of a material harder than at least the second main rubber elastic body 18 such as a synthetic resin is externally fitted and fixed to the axial center portion of the metal sleeve 54. Is embedded and fixed in the main rubber elastic body 18. The stopper ring 76 has a pair of stopper projections 78, 78 projecting radially outward at a height that does not reach the curvature 74 in the radial direction where the pair of curvatures 74, 74 face each other. Have. The protruding distal end surfaces of these stopper projections 78, 78 are radially opposed to the outer tube fitting 19 with the squeezing portion 74 interposed therebetween. Accordingly, when a large load is input in the radial direction corresponding to the vehicle longitudinal direction in which the spring characteristic is softened, the stopper projection 78 abuts on the outer cylinder 19 so that the inner cylinder 12 and the outer cylinder are in contact with each other. A stopper function for limiting the relative displacement of the metal fitting 19 (the outer cylindrical metal fitting 14) is exhibited.

The second main rubber elastic body 18 is integrally formed with a stopper rubber 80 projecting axially outward from the inner flange portion 60 of the outer tube fitting 19. And
As shown in FIG. 3, an annular plate-shaped stopper metal fitting 82 is bolted to the lower end of the rod 22 fixed to the inner cylindrical metal fitting 12 in a state of being mounted on the vehicle. The inner flange portion 60 of the outer tube fitting 19 is axially opposed to the stopper fitting 82, and the inner flange portion 60 is brought into contact with the stopper fitting 82 via the stopper rubber 80. , Outer tube fitting 19 (outer tube fitting 14) for inner tube fitting 12
Is limited in the amount of relative displacement downward in the axial direction (rebound direction).

In manufacturing the suspension member mount 10 having the above-described structure, for example, the following method is preferably employed.

First, as shown in FIG. 4, the first integral vulcanized molded product 37, the second integral vulcanized molded product 46, and the third integral vulcanized molded product 62 are separately separated in advance. After the vulcanization molding, the second integral vulcanization molding 46 is inserted into the first integral vulcanization molding 37 in the axial direction,
The fitting sleeve is press-fitted into the inner cylinder fitting 12 to be externally fixed, and the orifice cylinder fitting 44 is inserted into the outer cylinder fitting 14. Thereby, the first integrally vulcanized molded product 3
7 and the second integrally vulcanized molded product 46 are assembled to obtain an assembled body 84.

Next, the assembly 8 thus obtained is
4 is axially combined with the third integrally vulcanized molded product 62 so that the metal sleeve 54 is press-fitted into the inner cylinder fitting 12 and externally fixed thereto, and the outer cylinder fitting 19 is connected to the outer cylinder fitting 14. Extrapolate to Thereby, the first, second and third integrally vulcanized molded products 37, 46, 62 are integrally assembled.

More preferably, the assembly of the assembly 84 to the third integrally vulcanized molded article 62 is performed in an incompressible fluid, whereby the assembly is performed simultaneously with the assembly.
An incompressible fluid can be filled into the fluid chamber 68.

Thereafter, diameter reduction processing is performed on the outer tube fitting 19. As shown in FIG. 4, for example, as shown in FIG. 4, the outer diameter of the outer cylindrical member 19 is reduced by an eight-way drawing process or a 16-way drawing process using an appropriate drawing jig. This can be done advantageously by exerting a compressive force radially inward from. Then, by this diameter reduction processing, the outer tube fitting 19 is reduced in diameter, and the diameter reducing force is reduced.
4, the orifice cylinder 44 is fluid-tightly fitted to the outer cylinder 14 and the outer cylinder 14 is fluid-tightly fitted to the outer cylinder 19 by reducing the diameter. Let's fix it. Thereby, first,
At the same time as the second and third integrally vulcanized molded articles 37, 46, 62 are fixedly assembled, the first and second annular fluid chambers 7 are formed.
By forming 0 and 72, the intended suspension member mount 10 can be completed.

At the upper end of the aperture jig 86, an aperture projection 88 protruding toward the inner peripheral surface is formed, and the upper end where the aperture projection 88 is formed is more protruding than the central portion in the axial direction. The reduction ratio in the radial direction is set to be large. In particular, in the present embodiment, the aperture protrusion 88
Gradually projects with an inclined surface toward the upper end portion of the drawing jig 86, the protrusion height becomes maximum at the upper end portion, and a smooth round surface is formed at the protruding tip portion, and the drawing jig 86 has It is formed continuously in the circumferential direction.

By performing the above-described drawing process on the outer tube fitting 19 with the drawing jig 86, the outer tube member 19 has an upper end portion which is larger than the diameter of the entire cylindrical wall portion. However, the diameter is greatly reduced by the throttle projection 88, and the diameter reducing force is also exerted on the upper end portion of the outer cylindrical fitting 14. As a result, as shown in FIG. 1, the opening end of the outer cylindrical fitting 14 on the flange 34 side is reduced in diameter in the radial direction to be reduced in diameter, so that the outer cylindrical fitting 14 is reduced.
A concave portion 90 that is concave inward in the radial direction at the upper end portion is formed continuously in the circumferential direction. In addition, by reducing the diameter of the opening end on the flange portion 58 side of the outer tube fitting 19 in the radial direction so as to reduce the diameter, the upper end portion of the outer tube fitting 19 is formed in the concave portion 90 of the outer tube fitting 14. An engaging portion 92 that bends and projects radially inward toward the periphery is formed continuously in the circumferential direction.

The recess 90 and the engaging portion 92
Is formed, the suspension member mount 10 having the above-described structure can exhibit extremely excellent axial pull-out resistance between the outer tubular fitting 14 and the outer tubular fitting 19. is there. That is, as shown in FIG.
When an axial load is input between the inner cylindrical member 12 and the outer cylindrical member 19 in the mounted state, a relative axial displacement force is exerted between the outer cylindrical member 14 and the outer cylindrical member 19. It will be. At this time, the axial upward displacement of the outer tube fitting 19 relative to the outer tube fitting 14 is ensured by the fact that the flange 58 of the outer tube fitting 19 is in contact with the flange 34 of the outer tube fitting 14. Although it is prevented, the displacement in the direction in which the outer tube fitting 19 is pulled down from the outer tube fitting 14 in the axial direction becomes a problem. Here, in the suspension member mount 10 of the present embodiment, the locking action in the axial direction between the engaging portion 92 formed in the outer tube fitting 19 and the concave portion 90 formed in the outer tube fitting 14. By
Effective pull-out resistance is exerted between the outer tube fitting 14 and the outer tube fitting 19, so that excellent axial load resistance, reliability and durability can be realized.

In this embodiment, the outer tube fitting 14 is provided.
A fourth seal rubber layer 64 is interposed between the outer cylinder fitting 19 and the outer cylinder fitting 19.
4 is absorbed or buffered by the fourth seal rubber layer 64, so that the concave portion 9
0 and the shape of the engaging portion 92 of the insertion tube fitting 19 do not completely match. Further, since the fourth seal rubber layer 64 is interposed between the concave portion 90 and the engaging portion 92 by being pressed, the inner diameter of the engaging portion 92 is not necessarily smaller than the outer diameter of the concave portion 90. Even when the outer sealing member 14 is not subjected to the axial pulling force in the direction of pulling the outer cylindrical member 19 downward in the axial direction, the fourth seal rubber layer 64 is compressed between the engaging portion 92 and the concave portion 90. By being acted upon,
An effective pull-out resistance force is generated between the outer tubular fitting 14 and the outer tubular fitting 19 by a locking force or a frictional force between the concave portion 90 and the engaging portion 92 via the fourth seal rubber layer 64. It will be. In other words, the recess 9 of the outer cylinder fitting 14
0 and the engaging portion 92 of the outer tube fitting 19 are not necessarily overlapped in the axial direction.
With the concave portion 90 and the engaging portion 92 overlapped with each other, an effective pull-out resistance can be provided between the outer cylindrical member 14 and the outer cylindrical member 19.

Moreover, in the present embodiment, in particular, the concave portion 90 and the engaging portion 92 which provide such excellent pull-out resistance are provided.
However, in the drawing step of the outer tube fitting 19 conventionally used for fitting and fixing the outer tube member 19 to the outer tube member 14, the outer tube member 19 is formed at the same time by employing a specific drawing jig 86. Therefore, no special process or operation is required to form the concave portion 90 and the engaging portion 92, and excellent mount manufacturability is exhibited.

In addition, in this embodiment, the outer tube fitting 19
A flange portion 58 is formed on an opening peripheral portion on the upper end side in the axial direction of the outer cylinder 14. The flange portion 58 is superimposed on the flange portion 34 of the outer cylindrical metal fitting 14 and is externally fitted and fixed to the outer cylindrical fitting 19. Mounting sleeve 26 for member 24
The suspension member mount 10 is positioned with respect to the suspension member 24 by contacting the upper end surface in the axial direction with the lower surface of the flange portion 58. The inner diameter of the flange 58 is set smaller than the inner diameter of the mounting sleeve 26 of the suspension member 24 because the end of the flange 58 on the side of the flange 58 is reduced in diameter by the engaging portion 92. Therefore, the axial end surface of the mounting sleeve 26 is brought into contact with the radially intermediate portion of the flange portion 58 of the outer tube fitting 19, and the upper end corner of the outer tube member 19 where the flange portion 58 is bent. Since the rounded portion attached to the portion is positioned radially inward from the contact portion of the mounting sleeve 26, the flange portion 58 of the mounting sleeve 26 is formed by the rounded portion.
Therefore, a stable abutting state is advantageously realized without hindering the abutment with the, and excellent positioning accuracy is exhibited.

The embodiment of the present invention has been described in detail above, but this is merely an example.
The specific description of such an embodiment is not to be construed as limiting in any way.

For example, as shown in FIG. 5, the engaging portion 92 of the outer cylinder 19 is inserted into the recess 90 of the outer cylinder 14.
And the concave portion 90 and the engaging portion 92 are formed to overlap in the axial direction by setting the inner diameter dimension: φD of the engaging portion 92 smaller than the outer diameter size: φE of the outer cylindrical metal fitting 14. May be. Thus, the concave portion 90 and the engaging portion 92 exert a shape-locking action in the axial direction, so that a larger pull-out resistance can be obtained.

Further, as shown in FIG. 6, the flange portion 58 of the outer tube fitting 19 need not always be formed. In FIGS. 5 and 6, in order to facilitate understanding, members and parts having the same structure as those of the above-described embodiment are denoted by the same reference numerals as those of the above-described embodiment. Is attached.

Further, the present invention can be applied to a cylindrical vibration isolating assembly having no fluid chamber filled with an incompressible fluid. For example, a shaft member and an outer cylinder which are radially separated from each other. A cylindrical anti-vibration assembly having a structure in which members are connected by an elastic body of the main body and an externally inserted cylindrical metal fitting as a cylindrical bracket integrally formed with mounting legs and the like is externally fitted to the outer cylindrical member. And the like can be advantageously applied.

Even when the fluid chamber is formed, the specific structure of the fluid chamber, the orifice passage, and the like is appropriately determined according to the required vibration isolation characteristics and the like, and is not limited in any way. Not. For example, it has a structure in which a plurality of circumferentially divided fluid chambers are communicated with each other through an orifice passage so that an anti-vibration effect based on fluid flow action can be exerted against input vibration in a direction perpendicular to the axis. The present invention is similarly applicable to an anti-vibration assembly and the like.

Further, it is not always necessary to interpose a seal rubber layer between the fitting surfaces of the concave portion of the outer cylinder member and the engaging portion of the outer cylinder.

Further, the method of forming the engaging portion and the concave portion is not limited to the drawing process as illustrated, but may be formed by using, for example, a rolling roller or the like. Furthermore, the concave portion and the engaging portion are not necessarily formed at the same time, for example, using an outer cylindrical member in which a concave portion is formed in advance, and after externally inserting an external fitting having no engaging portion formed thereon. ,
It is also possible to form the engaging portion by bending the outer tube fitting toward the concave portion.

Furthermore, in the above-described embodiment, the axial length of the outer tubular fitting 19 or the axial length of the outer tubular fitting 14 is twice or more. However, depending on the structure of the vibration isolating assembly, etc. For example, the present invention can be similarly applied to an anti-vibration assembly having an outer cylindrical member and an outer cylindrical member having substantially the same axial length.

In addition, the present invention provides a cylindrical vibration isolator for a differential mount, a body mount, a subframe mount, a cab mount, a strut bar cushion, and other various mechanical devices in addition to the suspension member mount as illustrated. Of course, it is applicable to an assembly.

In addition, although not enumerated one by one, the present invention can be practiced in modes in which various changes, modifications, improvements, and the like are made based on the knowledge of those skilled in the art. It goes without saying that all of them are included in the scope of the present invention unless departing from the spirit of the present invention.

[0055]

As is apparent from the above description, in the fluid-filled cylindrical vibration damping assembly having the structure according to the present invention, the concave portion of the outer cylinder member and the engaging portion of the outer cylinder member are formed by the engagement portion. The pull-out resistance due to the locking force or the frictional force is effectively exerted, and the recesses and the engaging portions are formed by simply forming the outer cylindrical member and the outer cylindrical member with simple shapes. As a result, an improvement in the axial load bearing strength and durability can be advantageously achieved with excellent manufacturability and cost performance.

According to the method of the present invention, the concave portion of the outer cylindrical member and the engaging portion of the outer cylindrical member have a shape corresponding to each other with high precision, and the outer cylindrical member is fitted and fixed to the outer cylindrical member. Since the recess and the engaging portion are formed at the same time as the drawing process, a special processing step is not required for forming the concave portion and the engaging portion. This makes it possible to easily produce a cylindrical vibration-isolating assembly exhibiting force with extremely excellent manufacturability.

[Brief description of the drawings]

1 is a longitudinal sectional view of an automobile suspension member mount as one embodiment of the present invention, and is a view corresponding to a II section in FIG. 2;

FIG. 2 is a sectional view taken along the line II-II in FIG.

FIG. 3 is a longitudinal sectional view corresponding to FIG. 1, showing a state in which the suspension member mount shown in FIG. 1 is mounted on a vehicle.

FIG. 4 is a manufacturing process diagram for describing a method of manufacturing the suspension member mount shown in FIG.

FIG. 5 is a longitudinal sectional view showing a main part of a vehicle suspension member mount as another embodiment of the present invention.

FIG. 6 is a longitudinal sectional view showing a main part of a vehicle suspension member mount as still another embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Suspension member mount 12 Inner cylinder metal fitting 14 Outer cylinder metal fitting 16 First main rubber elastic body 18 Second main rubber elastic body 19 Extrapolated cylindrical metal fitting 34 Flange part 86 Restriction jig 88 Restriction projection 90 Recess 92 Engagement part

Claims (5)

[Claims] An outer tubular member having a flange portion at one opening peripheral edge portion in the axial direction is disposed at a distance from an outer peripheral side of the shaft member, and a main body is provided between the shaft member and the outer tubular member. A rubber elastic body is interposed, and the shaft member and the outer cylinder member are elastically connected, while an outer cylinder is externally fitted to and fixed to the outer cylinder member. In the vibration damping assembly, a concave portion that is recessed inward in a direction perpendicular to the axis is formed with respect to an axial end portion of the outer cylinder member on which the flange portion is formed, and the outer fitting of the outer cylinder member is formed. A cylindrical anti-vibration assembly, wherein an engaging portion bent inward in a direction perpendicular to the axis toward the concave portion is formed at an axial end portion located on the flange portion side. 2. A pocket portion, which is open to the outer peripheral surface, is formed on the rubber elastic body, and the external fitting is fixedly fitted to the outer tubular member via a seal rubber layer. 2. The cylindrical vibration isolating assembly according to claim 1, wherein the opening of the pocket portion is covered in a fluid-tight manner to form a fluid chamber in which an incompressible fluid is sealed. 3. The cylinder according to claim 1, wherein the engaging portion is positioned so as to enter into the concave portion so that the engaging portion and the concave portion overlap each other in the axial direction. Shaped anti-vibration assembly. 4. In the outer tube fitting, the engaging portion is formed continuously over the entire circumference in a circumferential direction, and the outer peripheral portion of the opening on the side where the engaging portion is formed is provided. The cylindrical vibration isolating assembly according to any one of claims 1 to 3, wherein a flange portion extending outward in a direction perpendicular to the axis is integrally formed, and the flange portion is overlapped with a flange portion of the outer cylindrical member. 5. When manufacturing the cylindrical vibration isolating assembly according to claim 1, the outer cylindrical member vulcanized and bonded to an outer peripheral surface of the main rubber elastic body. After extrapolating the outer tube fitting,
At the time of reducing the diameter of the outer tube member and fitting and fixing the outer tube member to the outer tube member, the amount of diameter reduction at the axial end of the outer tube member is made larger than that at the axial center portion to reduce And by applying such a diameter reducing force to the outer cylinder member, the concave portion of the outer cylinder member and the engaging portion of the outer tube fitting are formed at the same time. Manufacturing method of a cylindrical vibration isolating assembly.